US20180266520A1 - Shifting apparatus - Google Patents
Shifting apparatus Download PDFInfo
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- US20180266520A1 US20180266520A1 US15/707,254 US201715707254A US2018266520A1 US 20180266520 A1 US20180266520 A1 US 20180266520A1 US 201715707254 A US201715707254 A US 201715707254A US 2018266520 A1 US2018266520 A1 US 2018266520A1
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- United States
- Prior art keywords
- sleeve
- clutch gear
- gear teeth
- key
- shifting apparatus
- Prior art date
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- Abandoned
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- 230000000903 blocking effect Effects 0.000 claims description 38
- 230000008859 change Effects 0.000 claims description 9
- 238000006073 displacement reaction Methods 0.000 claims description 6
- 230000004044 response Effects 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 description 18
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000007935 neutral effect Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000007792 addition Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/025—Synchro rings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D2023/0618—Details of blocking mechanism comprising a helical spring loaded element, e.g. ball
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H2003/0818—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts comprising means for power-shifting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H2061/0425—Bridging torque interruption
- F16H2061/0429—Bridging torque interruption by torque supply with a clutch in parallel torque path
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
Definitions
- the present disclosure relates generally to a shifting apparatus that can be used in a vehicle transmission.
- a shifting apparatus of a vehicle comprises a synchronizer including: a hub rotationally confined to a shaft; a sleeve sliding relative to the hub in its axial direction; a transmission gear forming a speed change gear and rotatably installed at the shaft; a clutch gear provided integrally with the transmission gear and having a conical friction surface; and a synchronizer ring pressed by the sleeve against the conical friction surface of the clutch gear and thus performing a synchronizing action.
- the present disclosure proposes a shifting apparatus for use in an electric-vehicle transmission, which may reduce or eliminate torque interruption by allowing torque transmitted from a motor through an input shaft to be continuously transmitted to an output shaft during a shift, whereby the apparatus can provide efficient shifting operability and can achieve sufficient durability.
- a shifting apparatus includes: sleeve gear teeth provided on an inner circumferential surface of a sleeve; and clutch gear teeth provided on an outer circumferential surface of a clutch gear, the clutch gear teeth configured to engage with the sleeve gear teeth by movement of the sleeve in an axial direction, wherein ends of the sleeve gear teeth toward the clutch gear, and ends of the clutch gear teeth toward the sleeve form flat surfaces perpendicular to the axial direction.
- a friction cone may be integrally provided at the clutch gear, a blocking ring may be provided between the sleeve and the clutch gear, a counter cone is formed on an inner surface of the blocking ring, the counter cone configured to receive the friction cone, and a key may be radially elastically supported inside the sleeve.
- a sleeve groove is formed on the inner circumferential surface of the sleeve, and the sleeve groove is configured to allow a radial displacement of the key in response to the movement of the sleeve in the axial direction.
- the blocking ring may be provided with blocking inclined surfaces having a circumferential gap between the blocking inclined surfaces, and the circumferential gap is gradually narrowed in a radially inward direction such that when the blocking inclined surfaces are brought into contact with the key, an indexing torque is generated by a radially inward displacement of the key.
- the blocking ring may be provided with a pair of axial protrusions placed adjacent to each other and protruding toward the key, the pair of axial protrusions is configured to form the blocking inclined surfaces, and the blocking inclined surfaces may be formed on the pair of axial protrusions so as to face to each other.
- a key protrusion may be formed on a radial outer surface of the key and protrudes from a center of the key toward the inner circumferential surface of the sleeve in the axial direction, the key protrusion being inserted into the sleeve groove, and the key may be provided with counter-inclined surfaces on a radial inner surface thereof at circumferentially opposite sides to the key protrusion, the counter-inclined surfaces configured to receive the blocking inclined surfaces.
- a hub may be provided to constantly transmit and receive torque to and from an input shaft
- the clutch gear may be provided to transmit and receive torque to and from the input shaft regardless of an axial position of the sleeve relative to the clutch gear.
- a hub may be provided to constantly transmit and receive torque to and from an output shaft
- the clutch gear may be provided to transmit and receive torque to and from the output shaft regardless of an axial position of the sleeve relative to the clutch gear
- the clutch gear may be integrally connected to a speed change gear, and the speed change gear may be connected to a servo clutch so as to transmit torque to a shaft provided with the clutch gear.
- the input shaft may be directly connected to a motor.
- the present disclosure can be used in an electric-vehicle transmission that reduces or eliminates torque interruption or torque by allowing torque transmitted from a motor through an input shaft to be continuously transmitted to an output shaft during a shift, thereby providing efficient shifting operability and achieving sufficient durability.
- FIG. 1 is a view showing a configuration of a shifting apparatus in one form of the present disclosure
- FIG. 2 is a cross-sectional view showing an assembled state of the shifting apparatus in one form of the present disclosure
- FIG. 3 is a detailed view showing a main part of a blocking ring of FIG. 1 ;
- FIG. 4 is a detailed view showing a key of FIG. 1 ;
- FIGS. 5 and 6 are views showing examples of an electric-vehicle transmission to which the present disclosure can be applied;
- FIG. 7 is a view showing a process of engaging sleeve gear teeth with clutch gear teeth according to the present disclosure.
- FIG. 8 is a view showing a process of engaging sleeve gear teeth with clutch gear teeth in the prior art.
- a shifting apparatus in one form of the present disclosure comprises: sleeve gear teeth 3 provided on an inner circumferential surface of a sleeve 1 ; and clutch gear teeth 7 provided on an outer circumferential surface of a clutch gear 5 such that the clutch gear teeth 7 are engaged with the sleeve gear teeth 3 of the sleeve 1 by movement of the sleeve 1 in an axial direction.
- ends of the sleeve gear teeth 3 that face toward the clutch gear 5 and ends of the clutch gear teeth 7 that face toward the sleeve 1 form flat surfaces perpendicular to the axial direction.
- the ends of the sleeve gear teeth 3 and the ends of the clutch gear teeth 7 that face each other form flat surfaces parallel to each other rather than forming inclined chamfered surfaces.
- the axial direction means a longitudinal direction (i.e., the direction of a rotation center axis) of the sleeve 1 and the clutch gear 5
- a radial direction means a linear direction perpendicular to the rotation center axis
- a circumferential direction means a direction of an arc along a circumference of the sleeve 1 or the clutch gear 5 .
- a friction cone 9 is integrally provided at the clutch gear 5 , and a blocking ring 13 is provided between the sleeve 1 and the clutch gear 5 , and a key 15 is radially elastically supported inside the sleeve 1 .
- the blocking ring 13 is provided with a counter cone 11 on an inner surface of the blocking ring, and the counter cone 11 receives the friction cone 9 as illustrated in FIG. 2 .
- the sleeve 1 is provided, on the inner circumferential surface thereof, with a sleeve groove 17 that allows radial displacement of the key 15 in response to the movement of the sleeve 1 in the axial direction, and the blocking ring 13 is provided with blocking inclined surfaces 19 having a circumferential gap therebetween that is gradually narrowed in a radially inward direction such that when the blocking inclined surfaces 19 are brought into contact with the key 15 , an indexing torque is generated by radially inward displacement of the key 15 .
- the blocking ring 13 is provided with a pair of axial protrusions 21 placed adjacent to each other and protruding toward the key 15 to form the blocking inclined surfaces 19 , and the blocking inclined surfaces 19 are formed on the adjacent axial protrusions 21 to face to each other.
- the key 15 is provided with a key protrusion 23 protruding from a center of the key 15 toward the inner circumferential surface of the sleeve 1 in the axial direction, and being inserted into the sleeve groove 17 , and is provided with counter-inclined surfaces 25 on a radial inner surface thereof at circumferentially opposite sides of the key 15 to correspond to the blocking inclined surfaces 19 .
- FIG. 5 shows a configuration of an electric-vehicle transmission to which the present disclosure can be applied.
- a hub 27 is installed to constantly transmit and receive torque to and from an input shaft 29
- the clutch gear 5 is installed to transmit and receive torque to and from the input shaft 29 regardless of an axial position of the sleeve 1 relative to the clutch gear 5 .
- a hub 27 is installed to constantly transmit and receive torque to and from an output shaft 31
- the clutch gear 5 is installed to transmit and receive torque to and from the output shaft 31 regardless of the axial position of the sleeve 1 relative to the clutch gear 5 .
- the clutch gear 5 is integrally connected to a speed change gear, and the speed change gear is connected to a servo clutch 33 so as to transmit torque to a shaft provided with the clutch gear 5 .
- the clutch gear 5 is able to transmit and receive torque to and from the input shaft 29 or the output shaft 31 , respectively, regardless of the axial position of the sleeve 1 .
- Both the transmission of FIG. 5 and the transmission of FIG. 6 have a common configuration that the input shaft 29 is directly connected to a motor 35 , and a clutch gear to which the present disclosure is applied is the clutch gear 5 connected to the speed change gear connected to the servo clutch 33 .
- a first driving gear 37 is rotatably installed on the input shaft 29
- a first driven gear 39 is installed on the output shaft 31 in a state in which rotation thereof is restrained.
- a second driving gear 41 is rotatably installed on the input shaft 29
- a second driven gear 43 is installed on the output shaft 31 in a state in which rotation thereof is restrained.
- the input shaft 29 is provided with the shifting apparatus such as the hub 27 , the sleeve 1 , etc. to which the present disclosure is applied.
- first driving gear 37 the second driving gear 41 , the first driven gear 39 , and the second driven gear 43 are collectively referred to as a speed change gear.
- the second driving gear 41 is integrally connected with the clutch gear 5 to which the present disclosure is applied.
- the sleeve 1 In the process of shifting a first gear to a second gear in the transmission of FIG. 5 , the sleeve 1 is engaged with the clutch gear 5 connected to the first driving gear 37 to form a first-gear drive state. Then, when a shift command to the second gear is generated, the servo clutch 33 is controlled such that a part of power of the motor 35 is directly transmitted to the second driving gear 41 via the input shaft 29 . Thereafter, even when the sleeve 1 is released from the clutch gear 5 connected to the first driving gear 37 and forms a neutral state, torque is constantly transmitted from the motor 35 to the output shaft 31 , and thus torque interruption can be reduced or eliminated.
- the sleeve 1 presses the key 15 in the axial direction toward the second driving gear 41 such that the key 15 brings the blocking ring 13 into frictional contact with the friction cone 9 of the clutch gear 5 , by which synchronization is performed.
- the key 15 is pressed in the radially inward direction by the sleeve groove 17 of the sleeve 1 .
- Indexing refers to a condition where locking teeth provided on an outer circumferential surface of the synchronizer ring and sleeve gear teeth provided on an inner circumferential surface of a sleeve are aligned while inclined chamfered surfaces thereof slide relative to each other, whereby the sleeve gear teeth are allowed to move through the locking teeth toward the clutch gear teeth.
- performing the indexing means that the sleeve 1 is able to move toward the clutch gear 5 of the second driving gear 41 by aligning the blocking ring 13 with the key 15 while the key 15 moves in the radially inward direction with respect to the movement of the sleeve 1 in the axial direction.
- the sleeve 1 After the indexing, the sleeve 1 continues to move in the axial direction, such that the sleeve gear teeth 3 are engaged with the clutch gear teeth 7 . In the present disclosure, this state is shown in FIG. 7 .
- FIG. 7 shows a process in which ends of the sleeve gear teeth 3 and ends of the clutch gear teeth 7 come into contact with each other in a planar relationship, such that the sleeve gear teeth 3 are engaged with the clutch gear teeth 7 . It is shown that if a certain period of time has elapsed even in the state in which the ends of the sleeve gear teeth 3 are in contact with the ends of the clutch gear teeth 7 , the engagement is naturally performed by difference in the number of rotations between the sleeve 1 and the clutch gear 5 .
- the engagement state between the sleeve gear teeth 3 and the clutch gear teeth 7 is divided into two major ways.
- One is that the sleeve gear teeth 3 are aligned between clutch gear teeth 7 to be directly inserted therebetween, and the other is that as shown in FIG. 7 , the sleeve gear teeth 3 and the clutch gear teeth 7 come into contact with each other in a misaligned state, and then if a certain period of time has elapsed, they are engaged with each other at the moment of alignment due to the difference in the number of rotations.
- the second driving gear 41 is in a state where it can constantly transmit and receive torque to and from the output shaft 31 , and the sleeve 1 is directly connected to the motor 35 generating torque, whereby both the sleeve gear teeth 3 and the clutch gear teeth 7 are in a state of transmitting torque, which is different from a conventional shifting apparatus in which either the sleeve gear teeth 3 or the clutch gear teeth 7 is in a free-rotating state without transmitting torque to be synchronized with the remaining gear teeth.
- the conventional shifting apparatus includes a clutch gear teeth 7 and a sleeve gear teeth 3 , which correspond to those of the present disclosure (which will be described with the same name as the present disclosure for convenience), and each of them have inclined chamfered surfaces at ends thereof.
- the chamfered surfaces cause relative rotation, and thus efficient engagement can be performed.
- any one of the sleeve gear teeth 3 or the clutch gear teeth 7 should be in a state of freely rotating on the shaft without actively transmitting and receiving torque to and from the outside, so that the relative rotation can be achieved when only the inertia force is overcome. Accordingly, in the configuration in which both the sleeve gear teeth 3 and the clutch gear teeth 7 transmit torque as in the present disclosure, the problem as shown in FIG. 8 occurs.
- the shifting apparatus of the present disclosure may be also used in a transmission having the configuration of FIG. 6 , thereby performing the same operation as that of the transmission of FIG. 5 .
- the detailed description of the operation is omitted because it is almost the same as the transmission of FIG. 5 .
Abstract
Description
- This application claims priority to and the benefit of Korean Patent Application No. 10-2017-0033997, filed on Mar. 17, 2017, which is incorporated herein by reference in its entirety.
- The present disclosure relates generally to a shifting apparatus that can be used in a vehicle transmission.
- The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.
- In general, a shifting apparatus of a vehicle comprises a synchronizer including: a hub rotationally confined to a shaft; a sleeve sliding relative to the hub in its axial direction; a transmission gear forming a speed change gear and rotatably installed at the shaft; a clutch gear provided integrally with the transmission gear and having a conical friction surface; and a synchronizer ring pressed by the sleeve against the conical friction surface of the clutch gear and thus performing a synchronizing action.
- The foregoing is intended merely to aid in the understanding of the background of the present disclosure, and is not intended to mean that the present disclosure falls within the purview of the related art that is already known to those skilled in the art.
- The present disclosure proposes a shifting apparatus for use in an electric-vehicle transmission, which may reduce or eliminate torque interruption by allowing torque transmitted from a motor through an input shaft to be continuously transmitted to an output shaft during a shift, whereby the apparatus can provide efficient shifting operability and can achieve sufficient durability.
- In one aspect of the present disclosure, a shifting apparatus includes: sleeve gear teeth provided on an inner circumferential surface of a sleeve; and clutch gear teeth provided on an outer circumferential surface of a clutch gear, the clutch gear teeth configured to engage with the sleeve gear teeth by movement of the sleeve in an axial direction, wherein ends of the sleeve gear teeth toward the clutch gear, and ends of the clutch gear teeth toward the sleeve form flat surfaces perpendicular to the axial direction.
- A friction cone may be integrally provided at the clutch gear, a blocking ring may be provided between the sleeve and the clutch gear, a counter cone is formed on an inner surface of the blocking ring, the counter cone configured to receive the friction cone, and a key may be radially elastically supported inside the sleeve.
- A sleeve groove is formed on the inner circumferential surface of the sleeve, and the sleeve groove is configured to allow a radial displacement of the key in response to the movement of the sleeve in the axial direction. The blocking ring may be provided with blocking inclined surfaces having a circumferential gap between the blocking inclined surfaces, and the circumferential gap is gradually narrowed in a radially inward direction such that when the blocking inclined surfaces are brought into contact with the key, an indexing torque is generated by a radially inward displacement of the key.
- The blocking ring may be provided with a pair of axial protrusions placed adjacent to each other and protruding toward the key, the pair of axial protrusions is configured to form the blocking inclined surfaces, and the blocking inclined surfaces may be formed on the pair of axial protrusions so as to face to each other.
- A key protrusion may be formed on a radial outer surface of the key and protrudes from a center of the key toward the inner circumferential surface of the sleeve in the axial direction, the key protrusion being inserted into the sleeve groove, and the key may be provided with counter-inclined surfaces on a radial inner surface thereof at circumferentially opposite sides to the key protrusion, the counter-inclined surfaces configured to receive the blocking inclined surfaces.
- A hub may be provided to constantly transmit and receive torque to and from an input shaft, and the clutch gear may be provided to transmit and receive torque to and from the input shaft regardless of an axial position of the sleeve relative to the clutch gear.
- A hub may be provided to constantly transmit and receive torque to and from an output shaft, and the clutch gear may be provided to transmit and receive torque to and from the output shaft regardless of an axial position of the sleeve relative to the clutch gear.
- The clutch gear may be integrally connected to a speed change gear, and the speed change gear may be connected to a servo clutch so as to transmit torque to a shaft provided with the clutch gear.
- The input shaft may be directly connected to a motor.
- The present disclosure can be used in an electric-vehicle transmission that reduces or eliminates torque interruption or torque by allowing torque transmitted from a motor through an input shaft to be continuously transmitted to an output shaft during a shift, thereby providing efficient shifting operability and achieving sufficient durability.
- Further areas of applicability will become apparent from the description provided herein. It should be understood that the description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure.
- In order that the disclosure may be well understood, there will now be described various forms thereof, given by way of example, reference being made to the accompanying drawings, in which:
-
FIG. 1 is a view showing a configuration of a shifting apparatus in one form of the present disclosure; -
FIG. 2 is a cross-sectional view showing an assembled state of the shifting apparatus in one form of the present disclosure; -
FIG. 3 is a detailed view showing a main part of a blocking ring ofFIG. 1 ; -
FIG. 4 is a detailed view showing a key ofFIG. 1 ; -
FIGS. 5 and 6 are views showing examples of an electric-vehicle transmission to which the present disclosure can be applied; -
FIG. 7 is a view showing a process of engaging sleeve gear teeth with clutch gear teeth according to the present disclosure; and -
FIG. 8 is a view showing a process of engaging sleeve gear teeth with clutch gear teeth in the prior art. - The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.
- The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. It should be understood that throughout the drawings, corresponding reference numerals indicate like or corresponding parts and features.
- Referring to
FIGS. 1 to 7 , a shifting apparatus in one form of the present disclosure comprises:sleeve gear teeth 3 provided on an inner circumferential surface of asleeve 1; andclutch gear teeth 7 provided on an outer circumferential surface of aclutch gear 5 such that theclutch gear teeth 7 are engaged with thesleeve gear teeth 3 of thesleeve 1 by movement of thesleeve 1 in an axial direction. - Here, ends of the
sleeve gear teeth 3 that face toward theclutch gear 5 and ends of theclutch gear teeth 7 that face toward thesleeve 1 form flat surfaces perpendicular to the axial direction. - In other words, the ends of the
sleeve gear teeth 3 and the ends of theclutch gear teeth 7 that face each other form flat surfaces parallel to each other rather than forming inclined chamfered surfaces. - Here, the axial direction means a longitudinal direction (i.e., the direction of a rotation center axis) of the
sleeve 1 and theclutch gear 5, a radial direction means a linear direction perpendicular to the rotation center axis, and a circumferential direction means a direction of an arc along a circumference of thesleeve 1 or theclutch gear 5. - A
friction cone 9 is integrally provided at theclutch gear 5, and ablocking ring 13 is provided between thesleeve 1 and theclutch gear 5, and akey 15 is radially elastically supported inside thesleeve 1. Theblocking ring 13 is provided with acounter cone 11 on an inner surface of the blocking ring, and thecounter cone 11 receives thefriction cone 9 as illustrated inFIG. 2 . - The
sleeve 1 is provided, on the inner circumferential surface thereof, with asleeve groove 17 that allows radial displacement of thekey 15 in response to the movement of thesleeve 1 in the axial direction, and the blockingring 13 is provided with blockinginclined surfaces 19 having a circumferential gap therebetween that is gradually narrowed in a radially inward direction such that when the blockinginclined surfaces 19 are brought into contact with thekey 15, an indexing torque is generated by radially inward displacement of thekey 15. - As shown in detail in
FIG. 3 , theblocking ring 13 is provided with a pair ofaxial protrusions 21 placed adjacent to each other and protruding toward thekey 15 to form the blockinginclined surfaces 19, and the blockinginclined surfaces 19 are formed on the adjacentaxial protrusions 21 to face to each other. - As shown in detail in
FIG. 4 , thekey 15 is provided with akey protrusion 23 protruding from a center of thekey 15 toward the inner circumferential surface of thesleeve 1 in the axial direction, and being inserted into thesleeve groove 17, and is provided withcounter-inclined surfaces 25 on a radial inner surface thereof at circumferentially opposite sides of thekey 15 to correspond to the blockinginclined surfaces 19. - Meanwhile,
FIG. 5 shows a configuration of an electric-vehicle transmission to which the present disclosure can be applied. Ahub 27 is installed to constantly transmit and receive torque to and from aninput shaft 29, and theclutch gear 5 is installed to transmit and receive torque to and from theinput shaft 29 regardless of an axial position of thesleeve 1 relative to theclutch gear 5. - Further, in a configuration of the transmission of
FIG. 6 , ahub 27 is installed to constantly transmit and receive torque to and from anoutput shaft 31, and theclutch gear 5 is installed to transmit and receive torque to and from theoutput shaft 31 regardless of the axial position of thesleeve 1 relative to theclutch gear 5. - In the transmissions of
FIGS. 5 and 6 , theclutch gear 5 is integrally connected to a speed change gear, and the speed change gear is connected to aservo clutch 33 so as to transmit torque to a shaft provided with theclutch gear 5. Thus, theclutch gear 5 is able to transmit and receive torque to and from theinput shaft 29 or theoutput shaft 31, respectively, regardless of the axial position of thesleeve 1. - Both the transmission of
FIG. 5 and the transmission ofFIG. 6 have a common configuration that theinput shaft 29 is directly connected to amotor 35, and a clutch gear to which the present disclosure is applied is theclutch gear 5 connected to the speed change gear connected to theservo clutch 33. - In the transmission of
FIG. 5 , afirst driving gear 37 is rotatably installed on theinput shaft 29, and a first drivengear 39 is installed on theoutput shaft 31 in a state in which rotation thereof is restrained. Asecond driving gear 41 is rotatably installed on theinput shaft 29, and a second drivengear 43 is installed on theoutput shaft 31 in a state in which rotation thereof is restrained. Theinput shaft 29 is provided with the shifting apparatus such as thehub 27, thesleeve 1, etc. to which the present disclosure is applied. - Here, the
first driving gear 37, thesecond driving gear 41, the first drivengear 39, and the second drivengear 43 are collectively referred to as a speed change gear. Thesecond driving gear 41 is integrally connected with theclutch gear 5 to which the present disclosure is applied. - In the process of shifting a first gear to a second gear in the transmission of
FIG. 5 , thesleeve 1 is engaged with theclutch gear 5 connected to thefirst driving gear 37 to form a first-gear drive state. Then, when a shift command to the second gear is generated, theservo clutch 33 is controlled such that a part of power of themotor 35 is directly transmitted to thesecond driving gear 41 via theinput shaft 29. Thereafter, even when thesleeve 1 is released from theclutch gear 5 connected to thefirst driving gear 37 and forms a neutral state, torque is constantly transmitted from themotor 35 to theoutput shaft 31, and thus torque interruption can be reduced or eliminated. - When the
sleeve 1 is pressed toward thesecond driving gear 41 from the neutral state, thesleeve 1 presses thekey 15 in the axial direction toward thesecond driving gear 41 such that thekey 15 brings the blockingring 13 into frictional contact with thefriction cone 9 of theclutch gear 5, by which synchronization is performed. In addition, thekey 15 is pressed in the radially inward direction by thesleeve groove 17 of thesleeve 1. - The radially inward movement of the
key 15 is blocked by the frictional force between the blockinginclined surfaces 19 of the blockingring 13 and thecounter-inclined surfaces 25 of thekey 15 until synchronization is complete. When synchronization is completed, the indexing torque is generated by slidable relationship of the blockinginclined surfaces 19 and thecounter-inclined surfaces 25, and accordingly the blockingring 13 is slightly rotated with respect to thesleeve 1, whereby indexing is performed. - A shifting apparatus in which a synchronizer ring corresponding to the
blocking ring 13 is used is called indexing. Indexing refers to a condition where locking teeth provided on an outer circumferential surface of the synchronizer ring and sleeve gear teeth provided on an inner circumferential surface of a sleeve are aligned while inclined chamfered surfaces thereof slide relative to each other, whereby the sleeve gear teeth are allowed to move through the locking teeth toward the clutch gear teeth. Here, performing the indexing means that thesleeve 1 is able to move toward theclutch gear 5 of thesecond driving gear 41 by aligning the blockingring 13 with the key 15 while the key 15 moves in the radially inward direction with respect to the movement of thesleeve 1 in the axial direction. - After the indexing, the
sleeve 1 continues to move in the axial direction, such that thesleeve gear teeth 3 are engaged with theclutch gear teeth 7. In the present disclosure, this state is shown inFIG. 7 . -
FIG. 7 shows a process in which ends of thesleeve gear teeth 3 and ends of theclutch gear teeth 7 come into contact with each other in a planar relationship, such that thesleeve gear teeth 3 are engaged with theclutch gear teeth 7. It is shown that if a certain period of time has elapsed even in the state in which the ends of thesleeve gear teeth 3 are in contact with the ends of theclutch gear teeth 7, the engagement is naturally performed by difference in the number of rotations between thesleeve 1 and theclutch gear 5. - In other words, in the shifting apparatus of the present disclosure, the engagement state between the
sleeve gear teeth 3 and theclutch gear teeth 7 is divided into two major ways. One is that thesleeve gear teeth 3 are aligned betweenclutch gear teeth 7 to be directly inserted therebetween, and the other is that as shown inFIG. 7 , thesleeve gear teeth 3 and theclutch gear teeth 7 come into contact with each other in a misaligned state, and then if a certain period of time has elapsed, they are engaged with each other at the moment of alignment due to the difference in the number of rotations. - Although the above-mentioned direct engagement state is desirable, such state cannot always be formed but the state shown in
FIG. 7 is usually achieved. In this case, since the end portions of thesleeve gear teeth 3 and theclutch gear teeth 7 are in planar contact with each other, thesleeve gear teeth 3 and theclutch gear teeth 7 are inhibited or prevented from being broken or abraded when they are in contact with each other. Thus, it is expected that when a certain period of time has elapsed after the state shown inFIG. 7 is formed, gear engagement can be naturally and efficiently performed. - For reference, when the
sleeve 1 moves toward theclutch gear 5 after the indexing, the key 15 is displaced from thesleeve groove 17 and the force of the key 15 to bring the blockingring 13 into close contact with thefriction cone 9 of theclutch gear 5 is reduced. Accordingly, the synchronized state collapses for a short period of time and the relative speed between thesleeve 1 andclutch gear 5 is generated, whereby the engagement due to the speed difference between thesleeve gear teeth 3 and theclutch gear teeth 7 is possible as shown inFIG. 7 . - Moreover, in the engagement process shown in
FIG. 7 , thesecond driving gear 41 is in a state where it can constantly transmit and receive torque to and from theoutput shaft 31, and thesleeve 1 is directly connected to themotor 35 generating torque, whereby both thesleeve gear teeth 3 and theclutch gear teeth 7 are in a state of transmitting torque, which is different from a conventional shifting apparatus in which either thesleeve gear teeth 3 or theclutch gear teeth 7 is in a free-rotating state without transmitting torque to be synchronized with the remaining gear teeth. - In other words, according to the present disclosure, since a shift is performed while both the
sleeve gear teeth 3 and theclutch gear teeth 7 transmit torque, it is possible to obtain the effect of substantially reducing or eliminating torque interruption and to efficiently perform the shift. - In particular, in the operation of the conventional shifting apparatus as shown in
FIG. 8 , the conventional shifting apparatus includes aclutch gear teeth 7 and asleeve gear teeth 3, which correspond to those of the present disclosure (which will be described with the same name as the present disclosure for convenience), and each of them have inclined chamfered surfaces at ends thereof. Thus, when thesleeve gear teeth 3 are inserted betweenclutch gear teeth 7, the chamfered surfaces cause relative rotation, and thus efficient engagement can be performed. - However, in order to be able to perform engagement by causing the relative rotation by the chamfered surfaces as described above, any one of the
sleeve gear teeth 3 or theclutch gear teeth 7 should be in a state of freely rotating on the shaft without actively transmitting and receiving torque to and from the outside, so that the relative rotation can be achieved when only the inertia force is overcome. Accordingly, in the configuration in which both thesleeve gear teeth 3 and theclutch gear teeth 7 transmit torque as in the present disclosure, the problem as shown inFIG. 8 occurs. - In other words, in the case of
FIG. 8 , when the relative speed of thesleeve gear teeth 3 is faster than that of theclutch gear teeth 7 by Δω, thesleeve gear teeth 3 are in the state of transmitting torque of themotor 35. Accordingly, frictional force is continuously generated on the chamfered surfaces of both thesleeve gear teeth 3 and theclutch gear teeth 7, and the relative rotation of thesleeve gear teeth 3 with respect to theclutch gear teeth 7 does not occur. As a result, it is difficult to perform engagement, and the chamfered surfaces of thesleeve gear teeth 3 and theclutch gear teeth 7 may be broken. - Of course, in the case that torque of the
motor 35 is not transmitted to thesleeve gear teeth 3, and the shift is performed in a state where the input shaft is blocked by the clutch from the engine or the motor as in a conventional manual transmission vehicle, since thesleeve gear teeth 3 are not in a state of transmitting the torque, thesleeve gear teeth 3 rotate in an opposite direction relative to a rotation direction of theclutch gear teeth 7 while they slide relative to each other by the chamfered surfaces, whereby engagement is performed. - As described above, according to the present disclosure, efficient and stable engagement between the
sleeve gear teeth 3 and theclutch gear teeth 7 can be achieved in a transmission in which a shift is made while preventing torque interruption. Thus, it is possible to secure the shifting reliability and to secure the durability of thesleeve gear teeth 3 and theclutch gear teeth 7. - For reference, the shifting apparatus of the present disclosure may be also used in a transmission having the configuration of
FIG. 6 , thereby performing the same operation as that of the transmission ofFIG. 5 . The detailed description of the operation is omitted because it is almost the same as the transmission ofFIG. 5 . - Although exemplarly forms of the present disclosure have been described for illustrative purposes, those skilled in the art will appreciate that various modifications, additions and substitutions are possible, without departing from the scope and spirit of the present disclosure
Claims (11)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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KR10-2017-0033997 | 2017-03-17 | ||
KR1020170033997A KR20180107383A (en) | 2017-03-17 | 2017-03-17 | Shifting apparatus |
Publications (1)
Publication Number | Publication Date |
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US20180266520A1 true US20180266520A1 (en) | 2018-09-20 |
Family
ID=63519907
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US15/707,254 Abandoned US20180266520A1 (en) | 2017-03-17 | 2017-09-18 | Shifting apparatus |
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US (1) | US20180266520A1 (en) |
KR (1) | KR20180107383A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11480222B2 (en) * | 2020-02-19 | 2022-10-25 | Dana Automotive Systems Group, Llc | Electric drive axle system with a self-indexing clutch and method for operation of said clutch |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2398407A (en) * | 1944-07-13 | 1946-04-16 | Timken Detroit Axie Company | Power transmitting mechanism |
EP0976942A1 (en) * | 1998-07-31 | 2000-02-02 | IVECO FIAT S.p.A. | A synchronised clutch for the gearbox of a vehicle |
DE102010005316A1 (en) * | 2010-01-21 | 2011-07-28 | Daimler AG, 70327 | Form closure coupling device i.e. gear box coupling device, for drive train of motor car, has catch teeth including capture regions, where width of each catch tooth in capture regions is smaller than middle width of each clutch tooth |
US20110272234A1 (en) * | 2010-05-10 | 2011-11-10 | Hyundai Motor Company | Synchronizing Device for Transmission |
US20160053877A1 (en) * | 2014-08-22 | 2016-02-25 | Hyundai Motor Company | Transmission for electric vehicle |
-
2017
- 2017-03-17 KR KR1020170033997A patent/KR20180107383A/en unknown
- 2017-09-18 US US15/707,254 patent/US20180266520A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2398407A (en) * | 1944-07-13 | 1946-04-16 | Timken Detroit Axie Company | Power transmitting mechanism |
EP0976942A1 (en) * | 1998-07-31 | 2000-02-02 | IVECO FIAT S.p.A. | A synchronised clutch for the gearbox of a vehicle |
DE102010005316A1 (en) * | 2010-01-21 | 2011-07-28 | Daimler AG, 70327 | Form closure coupling device i.e. gear box coupling device, for drive train of motor car, has catch teeth including capture regions, where width of each catch tooth in capture regions is smaller than middle width of each clutch tooth |
US20110272234A1 (en) * | 2010-05-10 | 2011-11-10 | Hyundai Motor Company | Synchronizing Device for Transmission |
US20160053877A1 (en) * | 2014-08-22 | 2016-02-25 | Hyundai Motor Company | Transmission for electric vehicle |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11480222B2 (en) * | 2020-02-19 | 2022-10-25 | Dana Automotive Systems Group, Llc | Electric drive axle system with a self-indexing clutch and method for operation of said clutch |
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KR20180107383A (en) | 2018-10-02 |
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